Machine tool with automatic feed device



May 3, 1949.

, A. RICKENMANN MACHINE TOOL WITH AUTOMATIC FEED DEVICE 4 Sheets-Sheet 1 Filed July 51, 1947 llllllllllllll I III y 1949- A. RICKENMANN 2,469,077.

MACHINE TOOL WITH AUTOMATIC FEED DEVICE Filed July 31, 1947 4 Sheets-Sheet 2 May 3, 1949. A. RICKENMANN MACHINE TOOL WITH AUTOMATIC FEED DEVICE Filed July 51,1947

4 Sheets-Sheet 3 m I 1 m H mm May 3, 1949. A. RICKENMANN MACHINE TQOL WITH AUTOMATIC FEED DEVICE 4 Sheet-Sheet 4 Y Filed July 51', 1947 Patented May 3, 1949 UNITED PATENT OFFICE MACHINETGUL WITH AUTOMATIC FEED DEVICE .Klfred Rickenmann, Kus nacht, near Zurich,

Switzerland Appu'caticn :ruiy31, 1947, Serial No. 765,082 '14 claims. (01. 51-95) The inventionrelates to a machine tool, and particularly is directed to an automatic feed device for advancing the tool one step of predetermined distance toward the workpiece prior to each Working pass of the latter andfi-nally for the iast and final pass advancing the tool a distance which is automatically limited to :such an amount that th tool finishes the workpiece accurately to the desired size,

It is one "of the more important objects of the invention to provide a machinetool with anauto- 'matic feed device in which the total amount of feed of the tool is manually adjustable and may be subdivided into a *mber of individual feeding steps of which the first few may be uniform or when only two feeding steps are required the first one maybe greater than the last one.

At any rate the last "feeding step which is usually smaller, but never larger than the preceding feeding step, is automatically adjusted during the operation "of the machine 'tool to be of a size equal to the balance or the total amount of feed.

Another important object of the invention is a machine tool having a tool carriage previded with a manually rotatabl reed 'spi'ndle which is in threaded engagement with the tool carriage and which spindle has associated therewith an automatic feed device which prior to each workin pass of the workpiece moves the feed spindle, without rotating "it, in axial direction toward the workpiece.

It is also an object of the invention to provide a machine tool o'f the type having a longitudinally movable workpiece carriage which is moved by a guide spindle along the machine becl back and forth and past a transversely adjustable teol carriage with an electrically controlled and hydraulically operated feed mechanism which latter is automatically actuated each time the workpiece carriage reaches one end of its travel. The automatically actuated feed mechanism is provided with electrical and hydraulic control means which are arranged and. constructed in such a manner that the total amount of feed may be manually adjusted and may also be manually subdivided into a desired number of steps, each one of which is executed just prior to a working pass of the workpiece carriage past the tool carriage, where-- by the last feed step is automatically adjusted to an amount equal to the balance of the total feed prior to the beginning of the last working travel of the workpiece "carriage.

A further object of th invention is toprovide the automatic feed device of the machine tool therein the 2 of the type just described with means for automatioal'ly returning the workpiece carriage to its starting position after the tool has performed its last and finishing operation on the workpiece, and then stopping the driv of the guide spindle. Means are also provided for returning the automatic feed device to its initial positio-nrso that the completed workpiece may be removed and an"- other "one inserted.

Ancther obje'ct of the'invention is the combination or 'anautomatic feed device with a conventional rota-table feed spindle which is in threaded engagement with the tool carriage of a machine tool. The automatic feed device includes an exteriorly threaded sleeve axially slidably supported "in the machine frame and rotatably supporting reed spindle and engaging With one of its endsa shoulder on the latter, an in'teriorly threaded-sleeve which-engages the thread on said fir t mentioned sleeve and has an annular shoulder adapted to be drivingly engaged "by an end face of a feed gear when the latter durihg its rctation is urged by hydraulic pressure axially against said annular shoulder, so that the first mentioned sleeve and the feed spindle therein are moved -axiall in a direction towardtlre workp i'ece. Th feed gear is actuated by a ra'cl' on a hydraulically operated piston whose movement is limited by a manually adjustable stop which determines the amount cf feed of the tool hat-rriage for each pass with the exception of the last one. The automatic device of the invention may b'e'ihcerporated in macl'iinc tools 6f different types, but it is particularly adapted for grinding machines which are employed fer producing cylindrical workpieces or threaded wcrrpieees w 'ich have to be finished within very close toli rites.

It is, therefore, another object of the invention to provide a grinding machine, in fact, a screw thread grinding machine with an automatic feed device for the grinding tool thereof and which provides a cylindrical workpieize with a screw thread of predetermined size and prbfile in at least two passes, wherein prior to the last the reed. of the grinding tool is accurately and automatically adjusted so that the thread is finished with an accuracy which will be within the permissible limits.

Other purposes of the invention will be aparent from or will be specifically pointed out in the drawing forming a part of this specificatiorg but .it is to be understood that the invention is notlimited to the particular embodiment described and various forms may be adopted with in the scope of the claims.

between By Way of example there is described and illustrated in the following disclosure and drawings a thread grinding machine embodying the several features of th invention.

Referring to the drawings:

Fig. 1 is an elevation view of the machine tool for grinding threads.

Fig. 2 is a longitudinal sectional view of the machine tool and discloses diagrammatically the electrical and hydraulic control devices.

Fig. 3 is a cross sectional View of the upper portion of the machine tool substantially on the line II of Fig. 2.

Fig. 4 is a sectional View of the oil chamber of the control member, the feed piston and the feed limiting device, substantially on the line II--II of Fig. 3.

Fig. 5 is a sectional view of the brake associated with the feed device, substantially on the line III-III of Fig. 3.

Fig. 6 is a sectional view of the return mechanism substantially on the line IVIV of Fig. 3.

Fig. 7 is an elevation view of the feed adjusting and limiting device, partly in section substantially on the line V-V of Fig. 3.

Fig. 8 is a sectional view of the feed limiting device, substantially on the line VI-VI of Fig. 7, and

Fig. 9 is a sectional view of the manually operable adjusting mechanism for determining the individual feed steps of the automatic feed device, substantially on the line VIIVII of Fig. 2.

Referring to the drawings, particularly Figs. 1, 2 and 3, the machine frame I supports slidably in longitudinal guides 3 and 4 a workpiece carriage 2 which has mounted thereon a head stock 5 provided with two spaced bearings S and l for supporting the work spindle 8. The latter carries a worm wheel 9 and a driver ID for rotating the workpiece II. The workpiece H is rotatably supported between centers, namely the center l2, which is attached to one end of the work spindle .8, and the center 13 of a tail stock M mounted on the carriage 2.

A gear box IE is secured in the frame I of the machine tool and has attached thereto a flanged motor 18 which drives a shaft l1 extending into the gear box I5 and rotatably supported therein. The shaft H drives a set of change speed gears l8 which is axially slidable on shaft I1. Upon axial displacement of the gears I8 the same are adapted to selectively engage their respective companion gear in a set of integrally connected gears is mounted on a shaft 20. The center gear of the set of gears I9 is also in continuous driving engagement with a spur gear 2! rotatably mounted on a shaft 22. The shaft 22 carries rotatably thereon another spur gear 26. The gears 2| and 26 are mounted in axially spaced relation freely rotatable on the shaft 22 and the hubs of these gears face each other and are provided each with coupling teeth 2! and respectively. A coupling sleeve 23 is mounted by means of a key axially movable on the shaft 22 between the two gears 2! and 26. Both ends of the coupling sleeve 23 have coupling teeth which are adapted to be brought selectively in engagement with the coupling teeth 2N and 26 on the ears 2| or 26. A control lever 24 is mounted its ends rotatably on a stationary pin 25 within the gear box I 5 and one end of this lever 24 is operatively connected to the coupling sleeve 23. When the lever 24 is moved into the position illustrated in Fig. 2 the coupling sleeve 23 engages coupling teeth 2W of the gear 2! which latter is rotated by the change speed gear- 4 ing l8, l9 so that the coupling sleeve 23 is rotated and drives the shaft 22. This position of the coupling sleeve 23 indicates the operative position of the machine tool in which the work spindle 8 is rotated in a direction in which the workpiece is engaged by the tool.

During the reverse rotation of the work spindle 8 the coupling sleeve 23 is in e ga t t the coupling teeth 26 on the gear 26. In the last named position the shaft 22 will be driven in the opposite direction by the gear 26 which meshes directly with a gear 27 mounted on shaft l1.

The shaft 22 drives by means of the bevel gears 28 and 29 a telescoping shaft 3?), 3! which in turn drives a vertical shaft 32. The shaft 32 is rotatably supported in a bearing 33 of the head stock 5 and has mounted thereon a worm 34 which meshes with the worm wheel 9 attached to the work spindle 8.

The rear end of the work spindle 8 has keyed thereto a spur gear 35 which drives the gears 36, 37 and 38 which last named gear is mounted on the rear end of the guide spindle 39 of the machine. The four gears 35, 36, 37 and 38 are mounted in such a manner so as to be readily exchangeable and the ratio of the same in each case is selected according to the pitch of the thread which is to be ground on the workpiece. The guide spindle 39 is rotatably mounted in a bearing 43 of the carriage 2 and has collars 4i and 42 attached thereto which engage opposite end faces of the bearing and thereby prevent a relative axial movement of the guide spindle 39 with respect to the carriage 2. The threaded portion of the guide spindle 39 is in threaded engagement with a guide spindle nut 53 which is fixedly attached to the frame I of the machine.

A tool carriage 44 is slidably mounted in two guideways which are not shown but which extend at right angles to the guideways El and 4 of the workpiece carriage 2. The tool carriage 44 has mounted thereon a motor 45, Fig. 3, which by means of a small pulley 46 and the belt 4! drives a larger pulley 68 mounted on one end of a grinding wheel spindle 39. The other end of the spindle A9 has mounted thereon a grinding disc 50.

The tool carriage M, Fig. 3.. has attached thereto a flexible tape 52 which is guided over a guide roller 53 and carries a weight 54. The arrangement is such that the weight 56 urges the tool carriage M continuously rearwardly and away from the workpiece I l on the workpiece carriage 2.

The tool carriage M is operated by a feed spindle having a threaded portion 55!- in engagement with a nut 55 mounted on the tool carriage M. The feed spindle 55 is rotatably supported near its outer end, by a bearing 51 in the machine frame 5 and also by a sleeve 59 which surrounds the feed spindle 55 between its ends. The outer end of the feed spindle 55, which projects from the front side of the machine frame,

has keyed thereto a handwheel 53. The sleeve '59 is provided on a somewhat enlarged portion of its outer circumference with a thread 5% and is longitudinally movably mounted in a flanged bearing 62 which is attached by screws 6! to a wall l forming a portion of the machine frame I. A key 63 prevents a rotative movement of the sleeve 59 within the bearing 62. A second sleeve 64 which in the following will be designated with gear sleeve, because it has gear teeth 64! thereon is rotatably mounted on the sleeve 59 and is in threaded engagement with the thread 59l on the same. One endportion of the gear sleeve- 64 is provided with exterior gear teeth 64!. A reduced cylindrical portion 642 of the gear sleeve 65 supports rotatably a feed wheel provided on its outer circumference with gear teeth 653. Another still more reduced cylindrical portion 543 of the gear sleeve 64 has keyed thereto a'spur gear 66 which by means of a nut 61, screwed upon the outer end of the gear sleeve 64, is held in engagement with an annular shoulder 644 formed between the reduced cylindrical'portions 642 and 643, Fig. 3.

The hub 66! of the spur gear 65 is accurately machined and extends closely fitting into the enlarged bore f at one end of the feed wheel 65. In this manner there is produced between the flat radial bottom 652 of the bore 651 and the flat radial end face 652 of the hub 66! an annular chamber 58 whose inner cylindrical sur face is formed by a fraction of the outer circumference of" the reduced sleeve portion M2 and by a" portion of the wall of the bore 651.

Since the weight Ed urges the tool carriage M rearwardly it will be obvious that the feed spindle 55 also, which is in threaded engagement with the tool carriage M, is urged continuously rearwardly. The feed spindle 55 has between the sleeve 59 and the bearing 51 an enlarged portion or a collar 553 whose end face 552 is urged against an axial bearing 69 arranged between the right hand'end face 592 of the sleeve 3, and thec'ollar 553. Thesleeve 58 transmits its axial movement by means of its threaded portion 59! to the gear sleeve 64 and to an axial bearing 10' which latter is supported by the flanged bearing 62. The cylindrical end portion 6&5 of the gear sleeve id is embraced by a brake band ii, Figs. 3 and 5. One end of this brake band "H is attached to a bolt i2 and the other end of the brake band is attached to one end of a tension spring M having its other end attached to a bolt 73. The tension spring l' l maintains the brake band ll continuous engagement with the cylindrical portion 6 35 of the gear sleeve M. The two bolts '12 and '13 are attached to a wall of the machine frame i.

The gear teeth 6 5! of the gear sleeve E l mesh with rack teeth E5! of a tool carriage return piston 15 which is reciprocably mounted in a cylinder it the right hand end of which is closed We cover '51, Figs. 2 and 6.

The gear teeth 653 of the feed wheel 65 mesh with rack teeth 18!, Figs. 2, 3 and 4:, which are provided on a feed piston 18 mounted reciprocably in a cylinder "i9 which is arranged parallel to the cylinder Iii. The feed piston i8 is provided with an axial bore 582 in which is positioned a pressure spring Eli one end of which engages the bottom 133 of the bore I32 and the other end of which engages the cover 8! which closes the rear end of the cylinder it. The spring urges the feed piston it continuously toward the left, Figs. 2 4. The feed of the piston '58 as: represented by the distance H constitutes one ofthe initial feed movements of the tool and this distance is determined by the position of an abutment screw 82 which is threaded in the cover 553 and carries a worm wheel 32! and has a smooth cylindrical extension 822 which is slidably mounted in a bore 1-9! arranged in the lefthand end wall of the cylinder 19.

A manually operable adjusting mechanism is provided: for adjusting the position of the abutment screw: 82 and for changing the length of the feed movement H. This adjusti'ng. mechae nism is arranged at righta'ngles. to the center axis of the abutment screw: 82: and consists of. a shaft 84, Figs. 1 to 4 andiljournaledzin. bear; ing holes 85 and 86.: provided? in. the machine frame i, a worm wheel 81in engagement: with the worm wheel 82! and an adjusting'knob 88: attached to the outer endof the shaft 84; A collar 89 on the shaft 84 and the adjusting knobv 88 attached to the outer end. of the shaft 84' prevent an axial movement of the latter.

The desired feed movement. for eachpass: is obtained by adjusting the knob 88 which latter is provided with a scaleliil- By rotating the knob 83 the shaft 84 effects: a:corresponding'rotation' of the worm gearing 81,.8'2l. and therewith-J a rotative and axial movement of the. abutment screw 32. When theabutm'ent screw Blis moved toward the left the feed'movement-of the piston 18 will be increased while an adjustment of" the abutment screw d2 toward the right effectsv a decrease in the feed movement of the piston.

The spur'gear 66, Figs. land 3, which carries a stop 9!, meshes with a spur gear 92 which is keyed to a shaft t3 rotatablymounted in spaced bearings t t and -95 provided. in the" machine frame I. A drum 96 is lzeyedtoa reduced cylindrical portion 83! of the. shaft 93and is secured against axial movements by an annular nut 9'! which u ges the drum against an. annular shoulder $32 on the shaft '93.

The drum Elli, Figs. 3 and '7, carries two dogs 95 and E33, the first one of which. is rigidly secured while the other dog 99 is slidably adjustably mounted in a circular T-shaped groove of the drum. A stop i538 is fixedly attached by a' screw. or the like to the machine frame I.

An annular face iii! extends about the drum st and is provided with a scale Hi2, Fig. 7L ihe latter and the dogs 98 and Ed allow the adjustment and the limiting or the total distance 12 Fig. 3 which the tool carriage M has to move and of the rotary movement which the drum 9%. has to rotate in order to complete the grinding of one workpiece.

A double armed lever I03; Figs. 2, '7 and 8, is rotatably mounted on apinlMscrewed into the wall of the machine frame. A tension spring m5 attached with one end. to the lever arm iii-3i and with its other end to aflxed point of the machine frame urges the other arm W32. continuously in engagement with a'projection Niel. on a ring 1% as lon as thestop fill does not engage the lever arm iii3l.

The relative position and the ratio of the two spur gears 65 and 92 are: so selected that when the dog 9% engages the right hand side of the stop 5% the stop. iii presses upon thearm 5e34, whereby the inclined .fa'ce l033 on the arm I832 urges the bridging contact iiil on the switch pin iiiS against the two contactimenibers Hill and HM.

Prior to the beginning of thev grinding operation the total amount of feed t of the tool is determined and by means'of the scale 32 the automatic feed device is adjusted. For this purpose a crank or key is attached to the squared portion 933 of the shaft 93 and the latter with the drum at thereon is rotated in counter-clockwise direction until the line till-l on the fixedly attached dog 98 has been moved to a place on the scale I02 which corresponds to the desired total feed t. In this positionthedrum Q8 has been rotated about the angle a. and now the 'adfiustable dog as is slidably adjusted until itengagesthe-left hand side of the stop IIlIl. In this'position the dog 99 is clamped in position on the drum 95, Fig. 7. When the shaft 93 is rotated in the manner just'described the two meshing gears 92 and 66 are rotated and since the gear 65 is keyed to the gear sleeve 64 the latter is also rotated. The stop 9| attached to one end face of the gear 65 is thereby moved about the angle [3 away from its left hand end position, Fig. 1. The rotative movement of the gear sleeve 55, which is prevented from moving in axial direction, has the result that due to the left hand thread 591 the sleeve 59 is moved in axial direction rearwardly a distance corresponding to the amount of the total feed t which was adjusted on the scale I52. At the same time, the weight 54 which acts on the feed spindle 55 and on the tool carriage it moves the spindle 55 and the tool carriage is the sameamount rearwardly, that is, in a direction away from the workpiece carriage'z. I

A hydraulic device is used for controllin the machine. The hydraulically actuated controlling elements are assembled in the control block IIO. Furthermore, there are provided electrically actuated control devices which are supplied with electric energy from the main lines R and S. The operation of the control devices will be ex plained in the following:

Fig. 2 illustrates the machine during the execution of a working cycle. The couplin sleeve 23 is in engagement with the coupling teeth Zia of the gear 2|. Therefore, the motor It drives by means of the shaft I1 the set of change speed gears I8, the gear I9 on shaft 25, the gear 2!, the coupling sleeve 23, the shaft 22, the bevel gears 28, 29, the telescopic shaft 38, 3 I the vertical shaft 32 and by means of the worm earing 35', 9 the Work spindle 8. The latter rotates by means of the driver I5 the workpiece I I. The work spindle 8 drives also by means of the four suitably selected change speed gears 35, 36, 31 and 38 the guide spindle 39. The selection of the last named change speed gears takes place in correspondence with the pitch of the thread which is to be ground onto the workpiece II. The grinding disc 55 and the workpiece I I rotate in the direction of the arrows inserted in Figs. 1 to 3 and the workpiece carriage 2 moves from the left to the right because in this particular instance a right hand thread is to be ground.

The bridging contact III, Figs. 1 and 2, on the axially movable switch pin H2 of the electric switch I I3 which is secured to the machine frame I is in engagement with the contact elements I I4 and H5. I I3 an electric circuit is closed from the mainline R, the line H8, the contact member M6, the line II9, the contact member I I4, the bridging contact III, the contact member II 5, the line I25 which leads to the terminal I3! of the magnet coil I32, the other terminal I33 of which is connected by the line I34 with the other Imain line S. Therefore the magnet coil I32 is energized and in this position holds the rotatably mounted double armed lever I35 in the position in which it is shown in Fig. 2.

Furthermore, the main line R is connected by the line I36 with one terminal I 51 of a magnet coil I38 and the other terminal I39 of the magnet coil I38 is connected with the main line S by the line I45, the contact member I 43, the bridging contact I91 on the switch pin I08 which is in its working position, the contact member I42, the line I4I, the contact member I40 and the line IZI. Therefore, the magnet coil I38 is also ener- In this position of the electric switch gized'and holds the double arm "lever I 46 in the I position shown in Fig. 2.

The position of the double armed levers I35 and I46 which are connected by links I41 and I48 respectively, with control pistons I49 and I5Il respectively, create the following conditions in the hydraulic control system:

Oil under pressure, which in the example of the invention shown is forced by a gear pump I5I from a reservoir R1 into a line I53 over a pressure regulating valve I52, is conducted into the chamber I8I and from here through a passage I82 into the cylinder I 83. The pressur in th pipe line I53 is indicated by a pressure meter I55 connected to the pipe line I53 by a branch pipe I54. The cylinder I83 has slidably mounted therein a piston I84 and the oil pressure urges this piston into its upper end position in which the piston I 84 engages the cover I26. The piston I84 is provided at its lower end with a catch I22 and on its outer circumference is provided with a longitudinal groove I23 which terminates a short distance from the ends of the piston I85. A spring I25 is arranged in an axial bore I2 3 of the piston I84 and has the tendency to move the piston I84 downwardly, namely as soon as the pressure is released from the fluid in the cylinder I 33.

The pipe line I53 supplies also oil under pressure to a branch pipe I56 which leads to the chamber I51 and from the latter the oil under pressure is conducted through a passage I58 into a chamber I59 and urges the piston I60 therein continuously toward the right. The chamber IN on the right hand side of the piston I 60 is connected by a passage I62 with the reservoir R1. The piston rod I53 of the piston I60 is connected by a link I5 5 with the outer end of the double armed lever 24 and therefore as long as in this position of the parts the fluid in the chamber I59 is under pressure, the coupling sleeve 23 connected to the double armed lever 24 is held in operative engagement with the coupling teeth 2i of the rotating gear 2|. Some of the pressure fluid in the chamber I59 is conducted by a passage m5 into the longitudinal groove I23 of the piston I85 and flows from here into the passages I21 and I28 which are connected with a cylindrical chamber I66 to hold therein the piston I61 in its upper end position. A pressure spring I58 arranged in an axial bore of the piston I61 engages with its upper end the cover I59 which closes the upper end of the chamber I66 and has the tendency to move the piston I61 continuously downwardly. The chamber IE6 is also connected by a conduit IIil with the cylinder 19 and the pressure fluid entering the latter urges the feed piston 18 against the cover 8|.

The passage I21 is also connected with a branch conduit I1] which conducts pressure fluid into a radial bore I12, Fig. 3, of the feed spindle bearing 51 in the machine frame I. This radial bore I12 is connected with an annular groove in the feed spindle 55 and from this annular groove I13 the oil flows through a transverse bore I14 into an axial bore I15 of the spindle 55 to be con- .ducted to another transverse bore I16. The latter conducts the pressure fluid into another annular groove I11 which is connected with radial bores I18 in the sleeve 59 and with an exterior annular groove I19 which latter conducts the pressure fluid to the radial bores I80 in the gear sleeve 54 and into the annular chamber 68. The pressure fluid entering the annular chamber 68 urges the feedwheel axially against the annular shoulder "6% of the gear sleeve 64. At the end of the travel of the carriage 2 toward the right the adjustably mounted stop I85 on the carriage 2, Fig. 2, engages the switch pin H2 and moves the same toward the right. Thereby the bridging contact I l carried by the switch pin I12 opens the-electric circuit between the contact members -I Hi and H5 and shortly thereafter engages the two contact members I55 and Ill. The energization of the magnet coil I32 is thereby interrupted and the magnet coil I90 will now be energized by a circuit comprising the main line B, the line l 58, the contact member I It, the bridging contact I l l, the contact member H1 and the line I8? which is connected to one terminal I139 of the magnet coil @981. The other terminal 181 of the magnet coil ISii is connected b the line :52 with the terminal l3? and the line 534 with the otherrnain li S. As a result of the energization of the magnet coil I98 the double armed lever executes a rotative movement in clockwise direction and moves the piston I49 toward the right. lressure fluid from chamber i5? .flows .now into the passage i532 and into the chamber lfil and causes a movement of the piston 455 toward. the left. This movement of the piston I60 has the result that the piston rod Hi3 and the link connected thereto rotate the double armed lever 24 counterclockwise so that the coupling sleeve 23 is moved toward the right and comes into operative engagement with the coupling teeth 26a of the rotating gearfie. The shaft @2115 now rotated in the opposite direction by the motor it, the shaft ll of which drives the gears 2'7 and 25 and the coupling sleeve 23. Ween the shaft 22 in the manner described changes its direction of rotation the workpiece will also be rotated in the opposite direction and furthermore, the workpiece slide '3 moves from the right hand toward the left hand side.

The fluid in the chamber I59 can escape into the reservoir 31 over the passage 153. Furthermore, the oil in the annular chamber 58, Fig. 3 may escape through the bores I88), the annular groove i'iii, the bores ill, the transverse bore the axial bore I'll"), the transverse bore lit, the annular groove Il3, the bore H2, the conduit ill, the passage I21, the longitudinal groove I23 and the passage E55 into the chamber W8 and from here over the passage 3' 1 I58 into the reservoir R1. During the return travel of the carriage 2 the driving connection between the two end faces 5% and 6 1 5 of the feed wheel. and gear sleeve fi l respectively,

A.- Dr, us."

which was established by the pressure of the oil in the chamber 68, is released.

"The oil in the chamber lilii will be ejected by the piston if which moves downwardly under the influence or the spring 62. The ejected oil escapes over the passage 528 into the passage I23 which in thisphase of the operation leads theoil which 'isno longer under pressure toward the reservoir R1.

feed piston '28 -noves now under the influence of the spring 81 toward the left, Fig. l, until the ES engages the end face 823 of the abutment screw 82. The oil in the cylinder '59 will be ejected into the conduit ilil, into the branch conduit ass into the upper end of the chamber Ebb which by means of a drain passage it? is connected with the reservolnRi. piston '55 is moved. toward the .left a distance l-l, Fig. l, which represer s the i'feed movement of the toolfor one The rack on the feed piston it rotates the feed lit, the annuiar groove if gear (iii in unison gear a corresponding amount. However, it should be noted that during this rotative movement of the feed wheel 555 the adjacent gear sleeve (it and spur gear 66 will not be rotated but remain stationary because of the action of the brake ll and '54 which prevents any rotation of the last named parts.

At the end of the return movement of the carriage 2 another adjustably mounted stop I96 on the latter engages the switch pin H2 and moves the latter towards the left whereby the bridging contact i i I comes again in contact with the contact members H4 and H5. The energization of the magnet coil I99 is thereby interrupted, while the magnet coil I32 is again energized by the circuit previously described. The double arme lever 235 will be rotated counterclockwise, moves the piston I49 towards the left, and pressure fluid enters the passage I58 from the chamber E5? to fill the chamber i553 and to move the piston it?! therein toward the right. The double armed lever 25 rotates clockwise and moves the coupling sleeve 23 towards the left into operative engagement with the coupling teeth 21a of the gear 2i, while at the same time the operative engagement of the sleeve 23 with the gear 26 is broken. The carriage 2 again changes its direction of travel and moves again from the left toward the right. The oil .in chamber it! escapes over the passage I62 into the reservoir R1.

The oil pressure necessary to move the piston It!) is, however, not sufficient to move the piston Nil upwardly, which piston in this phase of the operation of the machine is held by the spring I88 in its lower end position. However, oil under pressure from the chamber I59 is conducted into the annular chamber 68 by means of the passage lot, the axial groove I23, the passage Hi, the branch conduit III, bore 112, annular groove H3, transverse bore I'M, axial bore Ilfi, transverse bore I15, annular groove ill, bores H8, annular groove H79 and the bores I39. Therefore, the feed wheel 65 is again drivingly clamped with its end face .654, Fig. 3, against the end face 646 of the gear sleeve '64. Only then, when the piston I68 has completed its movement toward the right end the feed wheel 65 engages completely the gear sleeve 64 and an increase in the oil pressure takes place. Thereupon, the piston 5E1 moves upwardly and oil under pressure from the chamber I66 enters the conduit ITO and the cylinder 19. Now the feed piston 18 is moved toward the right until it engages the cover 8 I During this movement of the feed piston 18 towards the right the rack on the piston 18 rotates the feed gear 65 counter-clockwise, Figs. 2 and 4. :Since there is established between the feed gear 35 and the gear sleeve 64 a driving connection which was already present prior to the beginning of the feed movement of the piston l8 there will now be effected a .rotative movement of the gear sleeve $4 and of the spur with the feed gear 55. The axial pressure exerted by the oil under pressure within the annular chamber so is substantially greater than the circumferential braking power of the brake ii, is. The rotative movement of the gear sleeve ed in counter-clockwise direction has the result that by means of the thread 59.] there is efiected a longitudinal movement of the sleeve 59 forwardly, that is, toward the workpiece. Accordingly, the axial bearing 69 and the radial face 552 on the collar 553 and therewith travel of the carriage 2.

11 the entire feed spindle 55 with the nut 56 on the tool carriage 94 with the grinding disc 50 thereon is moved closer toward the workpiece II.

During the rctative movement of the gear sleeve 64 the gear teeth 64I thereon move the rack 151 and therewith the return piston 15 toward the right, Figs. 2 and 6. Furthermore, the stop 9I, Fig. '7, moves toward its end position about an angle 'y, which angle corresponds to the feed movement H of the feed piston 18. The gear 92 which meshes with the gear 66 is rotated by the latter in clockwise direction and the shaft 93 and the drum 96 with the two dogs 98 and 99 thereon rotate in the same direction. The dog 98 moves about the angle 6 and moves toward the stationar stop I00. The angle 6 corresponds to the feed distance H of the feed piston 18.

The alternation between the working travel and the return travel of the carriage 2 and the succession of the feed movements of the tool carriage 44 takes place in the described manner until the end of the last butone return During each feed movement of the tool the feed piston 18 moves the adjusted feed distance H from left to right and the stop 9| and the dog 98 respectively, move closer to the end position about their corresponding angles 7 and 5.

At the end of the last but one return travel the dog 98 is spaced from the stationary stop I an angle 6 which angle is smaller or at any rate not larger than the angle 6. In order to produce on the workpiece II a thread of the desired depth t, Fig. 3, it is necessary in the above described example that the next feed movement be smaller than the preceding feed movements. This requirement will be accomplished automatically by the feed device of the present invention in that at the beginning of the last working pass the feed piston 18 does not execute the complete feed distance H which has been adjusted by the adjusting device 84, 88, 90 but is only moved a distance h which corresponds to the angle 6. When the dog 98 engages the stationary stop I86 the desired depth t of the thread has been obtained. The stationary stop I80 prevents any further rotation of the drum 96, the shaft 93, the gears 92, 66, the gear sleeve 64 and feed gear 65. The movement of the feed piston 18 is stopped and the latter is maintained in this arrested position before it can reach the cover 8| The last feed movement is the result of conditions as they are encountered after the last but one return travel has been completed and the balance of the feed movement still to be executed will be accurately the difference between the desired depth of the thread and the depth of the thread already produced.

During the last feed movement the stop 9| on the spur gear 66 has been rotated about the angle g in counter-clockwise direction and is positioned now also in its end position. At the end of this rotative movement the stop 9| engages the double armed lever I83 and rotates the same clockwise. Thereby the lever arm I032 is removed from the projection I06I and the inclined face I033 moves the switch pin I08 forwardly, Fig. 3. The bridging contact I01 moves away from the contact members I 42 and I43 and engages the contact members I 40 and I44 and the result is that the magnet coil I38 is deenergized. However, there is now established a conductive connection between the main line 8 and the terminal I98 of the magnet coil I99 as follows:

The main line S, the line I2 I, the contact member I40, the bridging contact I01, the contact member I44, and the line I91. The magnet coil I99 will not as yet be energized because there is still no connection of the terminal 200 with the main line R. The double armed lever I46 and the control piston I50 connected therewith remain at present in their present position. At the end of the last working pass, however, the stop I85 moves the switch pin II2 toward the right. Thereby the bridging contact III is disengaged from the two contact members H4 and H5 and thereby the magnet coil I32 becomes deenergized. The bridging contact III, however, engages now the contact members II6 and H1 and a circuit is closed which energizes the magnet coil I 90. The result of this actuation of the switch pin II2 carrying the bridging contact I II has been described in all its details previously and, therefore, is repeated in the following only briefly. Upon energiz'ation of the magnet coil I90 the double armed lever I35 is rotated in clockwise direction and moves the piston I 49 toward the right. As a consequence the piston I60 moves toward the left and rotates the double armed lever 24 anti-clockwise so that the coupling sleeve 23 moves in operative engagement with the coupling teeth 26a of the gear 26 and thereby the direction of travel of the carriage 2 is reversed. At the same time the rigid connection between the feed wheel and the gear sleeve 64 is released because the oil in the annular chamber 68 can drain ofi. Furthermore, the piston 18 whose rack 18I engages the feed gear 65 moves toward the left until it engages the end face 823 of the abutment screw 82 and thereby the feed gear 65 is rotated clockwise.

As soon as the bridging contact I l I engages the contact members I I6 and H1 the magnet coil I99 is also energized because a circuit is completed including the main line R, the line H8, the contact member H6, the bridging contact III, the contact member II1, the line I 81, the branch line 20I, the terminal 200, the coil I 99, the terminal I98, the line I91,,the contact member I44, the bridging contact I01, the contact member I40 and the line I 2| which leads to the other main line S. Accordingly the double armed lever I46 is also rotated in clockwise direction and by means of the link I48 moves the piston I50 toward the right. Oil under pressure flows now from chamber I8I into the conduit 202 and into the cylinder 16, Figs. 2 and 6. The return piston 15 is now actuated by the oil under pressure and moves at once toward the left and thereby rotates with its rack teeth 15I the gear sleeve 64, Fig. 3. The gear 66 which is keyed to this gear sleeve 64 rotates also and drives the gear 92, the shaft 93 and the drum 96. The gear sleeve 64 and the gear 66 thereon rotate in clockwise direction and under the influence of the weight 54 and the left handed thread 59I the sleeve 59, the feed spindle 55 and the tool carriage 44 are axially displaced in a direction rearwardly, that is, away from the workpiece I I. The gear 92, the

I shaft 93 and the drum 96 rotate counterclockwise. As soon as the dog 99 engages the left side of the stationary stop I00 any further movement of the piston 15 and the parts driven by the same is arrested. The dog 98 is now againin the same position as at the beginning of the work: ing operation and also the stop 9| on the gear 66 has assumed its initial position and, of course.

13 the tool slide 44 has also been returned to its starting position.

At the beginning or the rearward movement of the tool carriage 44 the stop 9i has disengaged the lever arm IIl3I and the tension spring IE5, Fig. I, rotates the lever i533 into its initial position in which the lever arm i832 engages the projection Illtl. The switch pin IE8, however remains in its forward position in which the bridging contact I01 engages the two contact members I40 and I44.

The oil in the cylinder I83 is ejected through the passage I82 by means of the piston I84 which is forced downwardly by the spring I25,

When the workpiece carriage 2 during its return travel reaches its left hand end position the stop I98 actuates the switch pin H2 and connects the bridging contact III with the contact members IM and IE5 that in a manner already described the magnet coil I32 is energized. The piston M9 is thereby moved toward the left and oil under pressure enters the chamber I59 and moves the piston its therein toward the right. As soon as the piston Itll reaches a central position within its chamber the catch M2 on the'lower end of the piston i8 1 enters a notch I29 in the piston I56 and stops its travel toward the right. Accordingly, the lever 2 remains in its center position in which the coupling sleeve 23 is completely out of engagement with either one q: the two gears El and 26. It is obvious that in this position of the coupling sleeve 23 the change speed gearing driven by the motor Iii is unable to transmit a rotative movement to the shaft22. The workpiece i I and the guide spindle 39 stand still and the workpiece carriage 2 remains in its left hand end position.

"The passage I55 connected with the chamber I59 is filled with oil under pressure but in this position of the piston I653 this oil is unable to enter the annular chamber 58 and the cylinder 19 of the feed device because the piston lad is in its lower end position in which the passage I2? is closed.

In this position of the machine tool the finished workpiece ii is removed and is replaced by another workpiece to be worked upon, The machine tool is started again for perforn..- g another working process by moving the push button I39 on the switch pin iilB inwardly. In doing this the bridging contact iii? is brought into engagement with the two contact members M2 and H53 and thereby a circuit is closed which contains the main line S, the line i2 the contact member iii), the line Hit, the contact member i i- 2, the bridg ing contact iil'l, the contact m mber M3, the line the terminal I39, the innet itS, the terminal I3! and the line 535 which is directly connected with the main line The magnet coil Hill is thereby energized. The lines leading to the terminals I58 and 211121 of the magnet coil like, however, are not energized by the main line S because the contact members and IM are not connected with each other. double armed lever Hit is rotated counter-clockwise and piston I5 3 moves toward the left. As soon as this movement of the piston Iiili is completed the oil in the cylinder it may drain off through the conduit EH32. At the'same time oil under pressure enters the cylinder I855 through the passage H32, the piston Iil i is moved upwardly and the catch I22 is withdrawn from the notch I29 oi the piston Hill and now the two passages W5 and lZ'l are again in communication with each other.

Since'the chamber I59 is under pressure the piston I can now complete its movement toward the right and this has the result that the coupling sleeve 23 is coupled with the gear 2| and now the work piece carriage 2 starts immediately to travel toward the right, that is, it executes its working travel. At the same time the feed of the tool is initiated as has already been described previously. First of all the feed gearfiiis pressed by the fluid under pressure in the annular chamber 68 against the annular shoulder 6455 of the feed gear sleeve es. Then the piston Itl'i, Fig. 2, moves upwardly and thereafter the feed piston I8 is moved toward the right which has the result that the sleeve 59 and the feed spindle are moved longitudinally toward t3 e right, Fig. 3, in order to move the tool ca iage it toward the workpiece II. During feed movement the dog 98 moves through an angle 5 and the stop 9! moves through an angle w toward their respective end positions.

From the foregoing i will be apparent that the automatic iced device of the invention is operatively associated with a 'conventional rotatable feed spindle which is in threaded engagement with a nut on the tool carriage, but that the automatic feed device does not interfere with the manual adjustment of the tool carriage when the feed spindle is rotated. The automatic feed device performs solely an axial displacement of the reed spindle without rotating the same. The total-amount or feed to be performed by the-'autm matic feed is adjustable and is determined by the position of the two dogs 5% and 59 on the drum Furthermore, the individual steps or subdivisions of the total amount of automatic feed are also adjustable by the manual operable device 83. individua steps neednot be uniform, but be manually changed by adjusting the abutment screw 8.2 during the operation of the machine tool, with the exception 'of the last step whose amount is determined by the do $8 on the drum 95.

What I claim is:

1. In a machine tool, in combination, a frame, means for supporting and rotating a workpiece lengthwise of said frame between centers, said means including a carriage reciprocable lengthwise of said frame; a tool carriage slidably'supported in said frame and movable transversely with respect to said workpiece supporting carriage, a tool mounted on said tool carriage, and transverse feed means for said tool carriage adapted to produce a predetermined total amount of feed of the tool carriage in at least two steps, said last named transverse feed means including means for adjusting the transverse feed movement of the tool carriage to a fixed fractional amount of the total feed at the start of each pass of the workpiece past said tool with the exception of the last one, said transverse feed means being also provided with means for automatically adjusting the transverse feed required for the last one of the steps in such a manner-that the desired predetermined total amount of the feed of the tool carriage is accurately obtained.

2. In a machine tool, in combination, -'a "frame, a carriage reciprocable lengthwise of the frame and having means thereon for supporting and rotating a workpiece lengthwise of saidframe'a tool. carriage slidably supported in said frame movable transversely with respect to said first mentioned carriage, transverse feed rneans for said tool carriage adapted to produce a predetermined total amount of feed of the toolbarriage in at least two working passes of said first named carriage, hydraulically operated :and elec 15 trically controlled means for actuating said transverse feed means at the end of each lengthwise movement of said workpiece carriage, said transverse feed means including means for adjusting the transverse feed movement of the tool carriage to a selectively fixed fractional amount of the total feed at the start of each of said working passes with the exception of the last one, said transverse feed means being also provided with,

means for automatically adjusting the transverse feed required for the last one of said working passes in such a manner that the desired predetermined total amount of feed of the tool carriage is accurately obtained, and manually operating means for adjusting the individual fractional transverse feed movements of the tool carriage, said manually operable means being associated with means for limiting the movement of said hydraulically operated means when it actuates said transverse feed means for execution of the last one of said working passes.

3. In a machine tool, in combination, a frame, a carriage reciprocable lengthwise of the frame and having means thereon for supporting and rotating a workpiece lengthwise of said frame, a tool carriage slidably supported in said frame and movable transversely with respect to said first mentioned carriage, a transverse feed means for said tool carriage adapted to produce a predetermined total amount of feed of the tool carriage in at least two working passes of said first named carriage, hydraulically operated and electrically controlled means for actuating said transverse feed means at the end of each lengthwise movement of said workpiece carriage, said transverse feed means including a feed spindle attached to said tool carriage, a sleeve supported non-rotatably, but axially movable in said frame and in which said feed spindle is rotatably mounted, collar means fixed on said feed spindle, means for urging said feed spindle in axial direction in which said collar means engages one end of said sleeve, a gear sleeve in threaded engagement with the exterior circumference of said axially movable sleeve, an abutment on said frame against which one end of said gear sleeve is urged to prevent it against axial movement, a feed gear rotatably mounted on said gear sleeve and engaging with one of its ends an annular shoulder formed on said gear sleeve, a hydraulic cylinder extending transversely to said feed spindle, a reciprocable piston in said hydraulic cylinder and having rack teeth engaging said gear to rotate the same when said piston is reciprocated, hydraulic means operatively connected with said hydraulic cylinder and acting axially upon said feed gear to urge the same against said annular shoulder of said gear sleeve to cause the latter to rotate with said feed gear in a direction in which the sleeve on said feed spindle is axially moved to feed the latter and therewith the tool carriage toward the workpiece a distance which is a fraction of the total amount of said predetermined feed, manually operable means for adjusting the length of the stroke of said piston, thereby determining the individual fractional transverse feed movements of said tool carriage, said manually operable means being associated with means for limiting the movement of said piston when the latter actuates the feed gear and therewith the gear sleeve and the feed spindle for iii) the execution of the last one of said working passes.

14, In a machine tool, in combination, a frame, acarriage reciprocable-lengthwise of the frame and having means thereon for supporting and rotating a workpiece lengthwise of said frame, a tool carriage slidably supported in said frame and movable transversely with respect to said first mentioned carriage, a transverse feed means for said tool carriage adapted to produce a predetermined total amount of feed of the tool carriage in at least two working passes of said first named carriage, hydraulically operated and electrically controlled means for actuating said transverse feed means at the end of each lengthwise movement of said workpiece carriage, said transverse feed means including a feed spindle attached to said tool carriage, a sleeve supported non-rotatably, but axially movable in said frame and in which said feed spindle is rotatably mounted, collar means fixed on said feed spindle, means for urging said feed spindle in axial direction in which said collar means engages one end of said sleeve, a gear sleeve in threaded engagement with the exterior circumference of said axially movable sleeve, an abutment on said frame against which one end of said gear sleeve is urged to prevent it against axial movement, a feed gear rotatably mounted on said gear sleeve and engaging with One of its ends an annular shoulder formed on said gear sleeve, a hydraulic cylinder extending transversely to said feed spindle, a reciprocable piston in said hydraulic cylinder and having rack teeth engaging said feed gear to rotate the same when said piston is reciprocated, hydraulic means operatively connected with said hydraulic cylinder and acting axially upon said feed gear to urge the same against said annular shoulder of said gear sleeve to cause the latter to rotate with said feed gear in a direction in which the sleeve on said feed spindle is axially moved to feed the latter and therewith the tool carriage toward the workpiece a distance which is a fraction of the total amount of said predetermined feed, and manually adjustable means for presetting the total transverse feed of said tool carriage including a rotatable stop disc provided with two angularly spaced and angularly adjustable stops, a fixed stop on said frame adapted to be engaged by said adjustable stops on said stop disc at the beginning of the first working pass and at the end of the last working pass respectively, and a geared connection between said gear sleeve and said rotatable stop disc, whereby the latter is rotated whenever the gear sleeve is rotated by said feed gear,

5. In combination with a manually rotatable feed spindle which is in screw threaded engagement with a tool carriage slidably mounted in a frame, an automatically operable feed means adapted to produce a predetermined amount of feed of the tool carriage in at least two separate feed steps, said feed means including a sleeve supported non-rotatably, but axially movable in said frame, said feed spindle being rotatably mounted in said sleeve, collar means fixed on said feed spindle, means for urging said feed spindle in axial direction in which said collar means engages one end of said sleeve, a gear sleeve in screw threaded engagement with an enlarged exterior portion of said axially movable sleeve, an abutment on said frame against which one end of said gear sleeve is urged to prevent an axial movement of the latter, a feed gear rotatably mounted on a smooth cylindrical portion of said gear sleeve and engaging with one of itsends an annular shoulder formed on said gear sleeve, a hydraulic cylinder extending transversely to said feed spindle, a reciprocable piston in said hydraulic cylinder and having rack teeth engaging said feed gear to rotate the same when said piston is reciprocated, hydraulic means operatively connected with said hydraulic cylinder and acting axially upon said feed gear to urge the same against said annular shoulder of said gear sleeve to cause the latter to rotate with said feed gear in a direction in which the sleeve on said feed spindle is axially moved to feed the latter and therewith the tool carriage a distance which is a fraction of the total amount of said predetermined feed, manually operable means for adjusting the length of the stroke of the feed piston to thereby determine the length of the individual feed movements of said tool carriage, said manually operable means being associated with means for limiting the movement of said piston when the latter actuates the feed gear and therewith the gear sleeve and the feed spindle during the execution of the last one of the fractional portions of the total feed.

6. In a grinding machine, in combination, a frame, means for supporting and rotating a workpiece lengthwise of said frame between centers, said means including a carriage reciprocable lengthwise of said frame; a tool carriage slidably supported in said frame and movable transversely with respect to said workpiece supporting carriage, a grinding wheel and means for driving the same on said tool carriage, and transverse feed means for said tool carriage adapted to produce a predetermined total amount of feed of the tool carriage in at least two grinding passes, said last named transverse feed means including means for adjusting the transverse feed movement of the tool carriage to a fixed fractional amount of the total feed at the start of each of the said grinding passes with the exception of the last one, said transverse feed means being also provided with means for automatically adjusting the transverse feed required for the last one of said grinding passes in such a manner that the desired predetermined total amount of feed of the tool carriage is accurately obtained.

'7. In a grinding machine, in combination, a frame, means for supporting and rotating a workpiece lengthwise of said frame between centers, said means including a carriage reciprocable lengthwise of said frame; a tool carriage slidably supported in said frame and movable transversely with respect to said workpiece supporting carriage, a grinding wheel and means for driving the same on said tool carriage, and transverse feed means for said tool carriage adapted to produce a predetermined total amount of feed of the tool carriage in at least two grinding passes, hydraulically operated and electrically controlled means for actuating said transverse feed means at the end of each lengthwise movement of said workpiece carriage, said last named transverse feed means including means for adjusting the transverse feed movement of the tool carriage to a selectively fixed fractional amount of the total feed at the start of each of said grinding passes with the exception of thelast one, said transverse feed means being also provided with means for automatically adjusting the transverse feed required for the last one of said grinding passes in such a manner that the desired predetermined total amount of feed of the tool carriage is accurately obtained, and manually operated means for adjusting the individual fractional transverse feed movements of said tool carriage, said manually operable means being associated with means for limiting the movement of said hydraulically 18 operated means when it actuates said transverse feed means for execution of the last one of said grinding passes.

8. In a grinding machine, in combination, a frame, means for supporting and rotating a workpiece lengthwise of said frame between centers, said means including a carriage reciprocable lengthwise of said frame, a tool carriage slidably supported in said frame and movable transversely with respect to said workpiece supporting carriage, a grinding wheel and means for driving the same on said tool carriage, and transverse feed means for said tool carriage adapted to produce a predetermined total amount of feed of the tool carriage at least two grinding passes, said transverse means including a feed spindle attached to said tool carriage, a sleeve supported non-rotatably, but axially movable in said frame and in which said feed spindle is rotatably mounted, collar means fixed on said feed spindle, means for urging said feed spindle in axial direction in which said collar means engages one end of said sleeve, a gear sleeve in threaded engagement with the exterior circumference of said axially movable sleeve, an abutment on said frame against which one end of said gear sleeve is urged to prevent it against axial movement, a feed gear rotatably mounted on said gear sleeve and engaging with one of its ends an annular shoulder formed on said gear sleeve, a hydraulic cylinder extending transversely to said feed spindle, a reciprocable piston in said hydraulic cylinder and having rack teeth engaging said feed gear to rotate the same when said piston is reciprocated, hydraulic means operatively connected with said hydraulic cylinder and acting axially upon said feed gear to urge the same against said annular shoulder of said gear sleeve to cause the latter to rotate with said feed gear in a direction in which the sleeve on said feed spindle is axially moved to feed the latter and therewith the tool carriage toward the workpiece a distance which is a fraction of the total amount of said predetermined feed, manually operable means for adjusting the length of the stroke of said piston, thereby determining the individual fractional transverse feed movements of said tool carriage, said manually operable means being associated with means for limiting the movement of said piston when the latter actuates the feed gear and therewith the gear sleeve and the feed spindle for the execution of the last one of said grinding passes.

9. In a grinding machine, in combination, a frame, means for supporting and rotating a workpiece lengthwise of said frame between centers, said means including a carriage reciprocable lengthwise of said frame, a tool carriage slidably supported in said frame and movable transversely with respect to said workpiece supporting carriage, a grinding wheel and means for driving the same on said tool carriage, and transverse feed means for said tool carriage adapted to produce a predetermined total amount of feed of the tool carriage in at least two grinding passes, said transverse feed means including a feed spindle attached to said tool carriage, a sleeve supported non-rotatably, but axially movable in said frame and in which said feed spindle is rotatably mounted, collar means fixed on said feed spindle, means for urging said feed spindle in axial direction in which said collar means engages one end of said sleeve, a gear sleeve in threaded engagement with the exterior circumference of said axially movable sleeve, an abutment on said frame against which 11, including brake means engaging said gear sleeve for preventing rotation of the same when said feed gear after execution of its feed stroke changes its direction of rotation, and means for releasing the pressure of said hydraulic means acting upon said feed gear when the piston operatively connected to said feed gear is returning to its initial position. 9

14. In a grinding machine according to claim 11, including a second hydraulic cylinder arranged parallel to said first mentioned hydraulic cylinder, a reciprocable piston in said second hydraulic cylinder and having rack teeth thereon meshing with gear teeth on said gear sleeve, and means operated by said geared connection at the end of the last grinding pass for admitting pres- 22 sure fluid to said second hydraulic cylinder to move the piston therein in a direction in which the gear sleeve is rotated to return the feed spindie and the automatically operable feed means to starting position.

ALFRED RICKENMANN.

REFERENCES CITED UNITED STATES PATENTS Name Date Durkee Sept. 15, 1925 Number 

